CN102112706B - Splined-shaft connection and valve mechanism with splined-shaft connection between camshaft and displaceable cam carriers - Google Patents

Splined-shaft connection and valve mechanism with splined-shaft connection between camshaft and displaceable cam carriers Download PDF

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Publication number
CN102112706B
CN102112706B CN200980130047.7A CN200980130047A CN102112706B CN 102112706 B CN102112706 B CN 102112706B CN 200980130047 A CN200980130047 A CN 200980130047A CN 102112706 B CN102112706 B CN 102112706B
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China
Prior art keywords
outer toothed
toothed portion
tooth
internal tooth
spline joint
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CN200980130047.7A
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Chinese (zh)
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CN102112706A (en
Inventor
M·德博莱策
S·登勒
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Audi AG
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Audi AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/34413—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using composite camshafts, e.g. with cams being able to move relative to the camshaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • F01L2013/0052—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction with cams provided on an axially slidable sleeve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/01—Absolute values
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
    • F16D2001/103—Quick-acting couplings in which the parts are connected by simply bringing them together axially the torque is transmitted via splined connections
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T403/00—Joints and connections
    • Y10T403/70—Interfitted members
    • Y10T403/7026—Longitudinally splined or fluted rod
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T403/00—Joints and connections
    • Y10T403/70—Interfitted members
    • Y10T403/7026—Longitudinally splined or fluted rod
    • Y10T403/7035—Specific angle or shape of rib, key, groove, or shoulder

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Valve Device For Special Equipments (AREA)
  • Gear Transmission (AREA)
  • Gears, Cams (AREA)

Abstract

The invention relates to a splined-shaft connection between a hollow shaft or hub (4) which is provided with an internal toothing system (10) and a shaft (3) which is provided with an external toothing system (12). In order to make radial play compensation in the splined-shaft connection or radial mounting and centring of the hollow shaft or hub (4) on the shaft (3) possible, it is proposed that the two toothing systems (10, 11) lie opposite one another over part of their length in the region of a tip-circle diameter (18a) and/or a root-circle diameter (18b) of the external toothing system (11) with a clearance fit (SP) and lie opposite one another in the region of adjacent tooth flanks (20, 19) of the internal and external toothing systems (10, 11) at a greater spacing (A), and that the two toothing systems (10, 11); lie opposite one another over another part of their length in the region of the adjacent tooth flanks (20, 19) of the internal and external toothing systems (10, 11) with a clearance fit (SP), whereas they lie opposite one another in the region of the tip-circle diameter (18a) and the root-circle diameter (18b) of the external toothing system (11) with radial play (KS, FS). The splined-shaft connection according to the invention is preferably arranged between a camshaft (3) and cam carriers (4) of a valve timing mechanism for gas exchange valves of an internal combustion engine, wherein cam carriers (4) can be displaced on the camshaft (3).

Description

Spline joint structure and there is the valve mechanism of this structure
Technical field
The present invention relates to a kind of spline joint structure (Zahnwellenverbindung) and a kind of (enter for engine breathing door, exhaust valve) valve mechanism/distribution device (Ventiltrieb), wherein, this spline joint structure is arranged on to be had hollow shaft or the hub part of internal tooth portion and has between the axle of outer toothed portion, wherein, this valve mechanism comprises that one has at least piecemeal the camshaft of outer toothed portion and multiplely has an internal tooth portion, the cam supporting member that the axially movable mode of energy guides on described camshaft not relatively rotating, wherein between camshaft and multiple cam supporting member that the axially movable mode of energy guides not relatively rotating on camshaft, be respectively equipped with described spline joint structure.
Background technique
Spline joint structure is shape sealed (formschl ü ssig) axle, hub linkage structure, and it is designed at two transmitting torques between the parts of common rotating shaft line rotation, and wherein common parts are axle parts and another parts are hub parts.In spline joint structure, give adjacent tooth by the flank of tooth by transmission of torque, the described flank of tooth in the situation that of two parts relative movement vertically, mutually recline in the mode of Spielpassung in may situation, causes along the relative movement of sense of rotation or circumferential direction between two parts due to the fluctuation of load or torque ripple avoiding.Normally involute tooth (DIN 5480) or straight tooth-shaped tooth portion (DIN 5481) of tooth portion, the i.e. outer toothed portion of axle and the internal tooth portion of hollow shaft or hub part of two engagements.
Known spline joint structure is the linkage structure of profile of tooth centering (according to profile of tooth centering), and wherein the flank of tooth is except for transmitting torque, also for making hollow shaft or hub part be centered in axle.Particularly for the flank profil of roll extrusion, but may between the tooth portion of two engagements, cause larger radial clearance due to manufacturing tolerances, this also can cause larger gap in linkage structure of profile of tooth centering between the opposed flank of tooth of the tooth of inside and outside tooth portion, and then causes relative movement along parts sense of rotation or circumferential direction in the time of the fluctuation of load or torque ripple.
Summary of the invention
Therefore the object of the invention is: improve spline joint structure and the valve mechanism of the described type of beginning, thereby realize the radial clearance compensation in spline joint structure, or realize hollow shaft or radial support and the centering of hub part on axle.
According to the present invention, described object realizes in the following manner: internal tooth portion and outer toothed portion are opposite with Spielpassung in the top circle of outer toothed portion and/or the region of root circle in a part for its length, and opposed with larger distance in the region of the flank of tooth of internal tooth portion and outer toothed portion, and, internal tooth portion and outer toothed portion are opposed with Spielpassung in the region of the flank of tooth of internal tooth portion and outer toothed portion on another part of its length, and opposed with radial clearance in the top circle of outer toothed portion and the region of root circle.
The present invention is based on following conception: by measure according to the present invention make two tooth portions for the region of transmitting torque with for the region of feeling relieved decoupling or be separated from each other in the axial direction.
Because outer toothed portion is more easily processed than internal tooth portion, so a kind of preferred design of the present invention proposes, internal tooth portion has identical profile in its whole length, and outer toothed portion is divided at least two portion's sections with different profiles on the axial direction of described axle.
Preferably, the in the situation that in two portion's sections, the number of teeth being identical, this or each portion's section for transmitting torque with this or each for compared with portion's section of feeling relieved, the width of the tooth of outer toothed portion is less more greatly and highly, to hollow shaft can be installed.
Another kind of preferred design of the present invention proposes, outer toothed portion is divided into three portion's sections with different profiles on the axial direction of described axle, wherein preferably an intermediate section is used for transmitting torque, and two portion's sections that are arranged on these intermediate section both sides are for directly supporting and radial centering.But may be also, outer toothed portion is divided into four portion's sections in couples with different profiles on the axial direction of described axle, wherein respectively have two portion's sections for transmitting torque, two portion's sections are for supporting and radial centering, wherein for portion's section of transmitting torque with replace each other for portion's section of radial centering.
The outer toothed portion of its axis has portion's section of different profiles advantageously separates by anodontia narrow cylindrical portion section, to facilitate the difference processing to each portion section.
Accompanying drawing explanation
Elaborate the present invention by embodiment illustrated in the accompanying drawings below.Wherein:
Fig. 1 illustrates the side elevation view of multiple parts of valve mechanism, this valve mechanism for the intake valve of three cylinders of 6 cylinder V-type engines to and there are multiple cam supporting members that can move on camshaft;
Fig. 2 illustrates the horizontal longitudinal sectional view along the medial axis of camshaft;
Fig. 3 illustrates the partial enlarged drawing of the camshaft in Fig. 2, and it has cam supporting member;
Fig. 4 illustrates the corresponding view with Fig. 3, and it shows the outer toothed portion of camshaft;
Fig. 5 is illustrated in first and the 3rd section of outer toothed portion of camshaft, the detailed view of the engagement of the tooth of this outer toothed portion between two teeth of the internal tooth portion of cam supporting member;
Fig. 6 is illustrated in second and the 4th section of outer toothed portion of camshaft, the detailed view of the engagement of the tooth of this outer toothed portion between two teeth of the internal tooth portion of cam supporting member.
Embodiment
In the accompanying drawings only part shown in valve mechanism 1 in, can regulate stroke and the timing of two intake valves that activated by camshaft 3 of each cylinder 2, this valve mechanism 1 for the intake valve of three cylinders 2 of V-type 6 cylinder diesel engine to and there is the camshaft 3 that is positioned at cylinder head housing top, that can be rotated to support on diesel engine.
In addition, valve mechanism 1 comprises that for each cylinder 2 or the every pair of intake valve one can axially movable mode not relatively rotating be arranged on cam supporting member 4 on camshaft 3 and for making cam supporting member 4 mobile final controlling element 5(Fig. 1 between two definite mobile positions that are spaced apart from each other vertically).The cam supporting member 4 of three hollow cylindrical has two cams that are spaced apart from each other vertically separately to 6,7 in periphery, and wherein each cam is to comprising two cam 8,9(Fig. 2 with different stroke profiles).Two cams to 6,7 separately to the roller acting in conjunction of the roller tappet (not shown) of supporting swingably of relevant intake valve.By moving axially of cam supporting member 4, can make as required roller and cam to two cams 8 of 6 or 7, a contact in 9, makes the stroke profile of described roller process cam 8,9 between each refunding of camshaft 3 once, makes roller tappet open the situation lower swing of valve at this.By the different stroke profiles of two cams 8,9, the mobile position of the stroke that can make each valve and timing and cam supporting member 4 relevant and with the stroke of the valve of other cylinder 2 and timing independently, for example change relatively with rotating speed.
For cam supporting member 4 can be moved vertically on camshaft 3, hollow cylindrical cam supporting member 4 has internal tooth portion 10 on week therein, a spline joint structure that can move axially relatively is engaged and formed between camshaft 3 and each cam supporting member 4 in this internal tooth portion 10 with the outer toothed portion 11 on camshaft 3, this spline joint structure is for transmitting torque between camshaft 3 and cam supporting member 4 and make cam supporting member 4 directly in camshaft 3 upper supports or centering.
For transmission of torque function and supporting centering function are separated, the outer toothed portion 11 of camshaft 3 has four portion's sections that are separated from each other in the axial direction 12,13,14,15 for each cam supporting member 4, described portion section has different flank profils in couples, and this point the best in Fig. 3 and Fig. 4 illustrates.Described four portion's sections 12,13,14,15 have different length and extend through one total length altogether separately, this total length is equivalent to the length of cam supporting member 4 substantially, wherein said portion section is all meshed with internal tooth portion 10, and this internal tooth portion has identical flank profil in its whole length.
Two portion's sections 13 and 15 of separating by portion's section 14 are for transmission of torque, and two portion's sections 12 and 14 of separating by portion's section 13 for make cam supporting member 4 directly radially be bearing on camshaft 3 and make cam supporting member 4 and camshaft 3 about the spin axis centering of camshaft 3.The flank profil of two portion's sections is preferably made simultaneously or is rolled into.
As shown in Figure 5 in the best, the flank profil of outer toothed portion 11 in portion's section 13 and 15 is matched with the flank profil of internal tooth portion 10 like this, make the tooth 16 of outer toothed portion 11 and the adjacent tooth 21 of the internal tooth portion 10 of each cam supporting member 4 of camshaft 3 opposed with Spielpassung along the flank of tooth 19,20 facing with each other, and between the tooth top 17 of tooth 16 and the opposed region of internal tooth portion 10, conventionally there is a bottom clearance KS along the tip diameter 18a of outer toothed portion 11, tooth 16 there is not contacted with 21.In addition, between the tooth top of the tooth 21 of internal tooth portion 10 and the opposed region of outer toothed portion 11, conventionally there is a gap FS along the root diameter 18b of outer toothed portion 11, make that tooth 21 is same with 16 there does not contact.As in traditional gear, bottom clearance KS and root gap FS are m 0.1～0.3 times, wherein " m " is the modulus of outer toothed portion 11.
As shown in Figure 6 in the best, the flank profil of outer toothed portion 11 in portion's section 12 and 14 is matched with the flank profil of internal tooth portion 10 like this, make the tooth 16 of outer toothed portion 11 utilize its tooth top 17 opposed with Spielpassung SP and internal tooth portion 10 along a part of the tip diameter 18a of outer toothed portion 11, and tooth 16 along its (each other) back to the flank of tooth 19 with the corresponding opposed flank of tooth 20 of the tooth 21 of internal tooth portion 10 at a distance of a larger distance A.Determine like this size of this distance A, make not contact on the flank of tooth 19,20 of tooth 16,21.Under any circumstance, distance A is all obviously greater than the upper limit of Spielpassung SP or upper gap (maximal clearance) and is preferably also greater than bottom clearance KS, is greater than 0.1～0.3 times of m.
Alternatively or additionally, the tooth 21 of internal tooth portion 10 can utilize its tooth top opposed with Spielpassung SP and internal tooth portion 10 along a part of the root diameter 18b of outer toothed portion 11 in the corresponding way, and tooth 21 along its (each other) back to the flank of tooth 20 with the corresponding opposed flank of tooth 19 of the tooth 16 of outer toothed portion 11 at a distance of a larger distance A.The same size of determining this distance A, makes not contact on the flank of tooth 20,19 of tooth 21,16.Under any circumstance, distance A is all obviously greater than the upper limit of Spielpassung SP or upper gap and is preferably also greater than root gap FS, is greater than 0.1～0.3 times of m.
Spielpassung SP that exist in all portions section, between two tooth portions 10,11 allow cam supporting member 4 to move axially on camshaft 3.Adjacent portion's section 12,13 or 13,14 or 14,15 is separated by the anodontia narrow ring portion section 22 of camshaft 3 respectively.
On camshaft 3, form outer toothed portion 11 by following manner: first roll out two pairs of portion's sections 12 and 14 and 13 and 15 with different profiles, wherein two of tooth 16 each other back to the distance of 19 of the flank of tooth large in portion's section 13 and 15 than in portion's section 12 and 14.
In the case of the tip diameter 18 radial support cam supporting members 4 of the outer toothed portion 11 along camshaft 3, in portion's section 13 and 15, carry out after roll extrusion, the additionally tooth top 17 of grinding tooth 16, this is because can not enough accurately make the tip diameter 18 of the outer toothed portion 11 of camshaft 3 in roll extrusion.
For this reason, the root diameter 18b radial support of the preferred outer toothed portion 11 along camshaft 3 of cam supporting member 4, because the opposed tip diameter of the root diameter 18b of the outer toothed portion 11 of camshaft 3 and the internal tooth portion 10 of each cam supporting member 4 can be rolled in good condition.
When needed, make cam supporting member 7 on camshaft 4, move to vertically one of two definite mobile positions to regulate stroke and/or the timing of relevant intake valve 2, and always in the time that cam is opposed to the roller of 8,9 basic circle portion section and relevant tappet, carry out described movement.For mobile operation of actuator 5 respectively, this final controlling element 5 has two driving component/actuator 23(Fig. 1 that are arranged side by side), this driving component 23 can stretch out from final controlling element 5.In the time of operations actuator 5, one of two driving components 23 join in the spiral slot 24 of the left-handed or dextrorotation in the periphery of cam supporting member 4 in the time stretching out, this spiral slot 24 is opposed with the driving component 23 engaging in one of two mobile positions, so that cam supporting member 4 is camshaft 3 moving to the left or to the right in another mobile position by spiral slot 24 due to the motion of driving component 23 in turning subsequently.
Distance between two mobile positions is equivalent to each cam to 8,9 the centre distance of two cams 10,11 and the axial distance (Fig. 3) of two lock grooves 25,26, and described lock groove was formed near the interior week end of each cam supporting member 4.Two lock grooves 25,26 are for being locked at cam supporting member 4 two definite mobile positions.Described locking is realized by following manner: the power by helical compression spring 29 is pressed against the locking ball 28 being arranged in the transverse holes 27 of camshaft 4 on the inclined side of one of two grooves 25,26, thereby axial force component is directed in cam supporting member 4, and then cam supporting member 4 is pressed against to being used as on the end face 30 of blocked part, if the best is shown in Fig. 3 and Fig. 4 of adjacent rotated bearing 31.
Camshaft 4 drives by the sprocket wheel 32 on the end at camshaft 4, and gear 33 on contrary end drives an A axle.
Reference numerals list
1 valve mechanism
2 cylinders
3 camshafts
4 cam supporting members
5 final controlling element
6 cams pair
7 cams pair
8 cams
9 cams
10 internal tooth portions
11 outer toothed portion
Portion's section of 12 outer toothed portion
Portion's section of 13 outer toothed portion
Portion's section of 14 outer toothed portion
Portion's section of 15 outer toothed portion
The tooth of 16 outer toothed portion
17 tooth tops
The tip diameter of 18a outer toothed portion
The root diameter of 18b outer toothed portion
The flank of tooth of 19 outer toothed portion
The flank of tooth of 20 internal tooth portions
The tooth of 21 internal tooth portions
22 annular section
The driving component of 23 final controlling element
24 spiral slots
25 lock grooves
26 lock grooves
The transverse holes of 27 camshafts
28 locking balls
29 helical compression springs
30 stop surfaces
31 rotary bearings
32 sprocket wheels
33 gears

Claims (13)

1. a spline joint structure, this spline joint structure is arranged on to be had hollow shaft (4) or the hub part of internal tooth portion (10) and has between the axle (3) of outer toothed portion (11), it is characterized in that, described internal tooth portion (10) and outer toothed portion (11) are opposite with Spielpassung (SP) in the tip diameter (18a) of described outer toothed portion (11) and/or the region of root diameter (18b) in a part for its length, and at the adjacent flank of tooth (20 of described internal tooth portion (10) and outer toothed portion (11), 19) opposed with larger distance (A) in region, and, described internal tooth portion (10) and outer toothed portion (11) on another part of its length at the adjacent flank of tooth (20 of described internal tooth portion (10) and outer toothed portion (11), 19) opposed with Spielpassung (SP) in region, and in the tip diameter (18a) of described outer toothed portion (11) and the region of root diameter (18b) with radial clearance (KS, FS) opposed.
2. spline joint structure according to claim 1, is characterized in that, described distance (A) is greater than the upper limit of described Spielpassung (SP) and/or is greater than described radial clearance (KS, FS).
3. spline joint structure according to claim 2, is characterized in that, described radial clearance (KS, FS) is 0.1～0.3 times of m, and wherein said m is the modulus of described outer toothed portion (11).
4. according to spline joint structure in any one of the preceding claims wherein, it is characterized in that, described internal tooth portion (10) has identical profile in its whole length.
5. spline joint structure according to claim 1 and 2, is characterized in that, described outer toothed portion (11) is in axial direction divided at least two portion's sections (12,13,14,15) with different profiles.
6. spline joint structure according to claim 5, is characterized in that, the width of the tooth (16) of described outer toothed portion (11) is larger in ratio another (13,15 or 12,14) in described two portion's sections in one (12,14 or 13,15) of two portion's sections.
7. spline joint structure according to claim 5, is characterized in that, the height of the tooth (16) of described outer toothed portion (11) is less in ratio another (13,15 or 12,14) in described two portion's sections in one (12,14 or 13,15) of two portion's sections.
8. spline joint structure according to claim 1 and 2, it is characterized in that, described outer toothed portion (11) is divided into three or four portion's sections (12 in the axial direction, 13, 14, 15), wherein, described internal tooth portion (10) and outer toothed portion (11) are at the adjacent flank of tooth (20 of described internal tooth portion (10) and outer toothed portion (11) therein, 19) in region with the both sides of the opposed section of Spielpassung (SP) (13), be provided with wherein said internal tooth portion (10) and outer toothed portion (11) in the tip diameter (18a) of described outer toothed portion (11) and/or the region of root diameter (18b) with the opposed section (12 of Spielpassung (SP), 14).
9. spline joint structure according to claim 1 and 2, it is characterized in that, described outer toothed portion (11) is divided into three or four portion's sections (12 in the axial direction, 13, 14, 15), wherein, therein described internal tooth portion (10) and outer toothed portion (11) in the tip diameter (18a) of described outer toothed portion (11) and/or the region of root diameter (18b) with the both sides of the opposed section of Spielpassung (SP) (14), be provided with wherein said internal tooth portion (10) and outer toothed portion (11) the adjacent flank of tooth (20 in described internal tooth portion (10) and outer toothed portion (11), 19) in region with the opposed section (13 of Spielpassung (SP), 15).
10. spline joint structure according to claim 1 and 2, is characterized in that, described outer toothed portion (11) is divided into four portion's sections (12,13,14,15) on the axial direction of described axle, wherein every two portion's sections (12,14 with different profiles; 13,15) replace in couples.
11. spline joint structures according to claim 5, is characterized in that, adjacent portion's section (12,13,14,15) by narrow cylindrical portion section (22) separately.
12. spline joint structures according to claim 5, is characterized in that, described each portion section (12,13,14,15) has different axial lengths at least partly.
13. 1 kinds of valve mechanisms (1) for the ventilation door of motor, comprise one have at least piecemeal outer toothed portion (11) camshaft (3) and multiple have internal tooth portion (10), can axially movable mode not relatively rotating at the cam supporting member (4) of the upper guiding of described camshaft (3), it is characterized in that, between the formation main camshaft (3) of axle and the described cam supporting member (4) of each formation hollow shaft or hub part, be provided with according to spline joint structure in any one of the preceding claims wherein.
CN200980130047.7A 2008-07-31 2009-07-11 Splined-shaft connection and valve mechanism with splined-shaft connection between camshaft and displaceable cam carriers Active CN102112706B (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE200810035935 DE102008035935A1 (en) 2008-07-31 2008-07-31 Toothed shaft connection and valve drive with toothed shaft connection between a camshaft and displaceable cam carriers
DE102008035935.1 2008-07-31
PCT/EP2009/005057 WO2010012371A1 (en) 2008-07-31 2009-07-11 Splined-shaft connection and valve timing mechanism with a splined-shaft connection between a camshaft and displaceable cam carriers

Publications (2)

Publication Number Publication Date
CN102112706A CN102112706A (en) 2011-06-29
CN102112706B true CN102112706B (en) 2014-06-25

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CN200980130047.7A Active CN102112706B (en) 2008-07-31 2009-07-11 Splined-shaft connection and valve mechanism with splined-shaft connection between camshaft and displaceable cam carriers

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CN102112706A (en) 2011-06-29
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JP2011529552A (en) 2011-12-08
ATE536465T1 (en) 2011-12-15

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